Cooling device, cooling system, and auxiliary cooling device for datacenter

ABSTRACT

A cooling system for a data center, in which a plurality of servers having exothermic electronic components is installed in a housing. The cooling system comprises: a cooling circuit, a main cooling device to cool cooling medium heated by electronic components, and an auxiliary cooling device to assist the main cooling device in cooling the cooling medium.

The present invention claims the benefit of Japanese Patent Applications No. 2010-91680 filed on Apr. 12, 2010, No. 2010-94108 filed on Apr. 15, 2010, No. 2010-99071 filed on Apr. 22, 2010, No. 2010-121954 filed on May 27, 2010, No. 2011-41903 filed on Feb. 28, 2011 and No. 2011-41904 filed on Feb. 28, 2011 with the Japanese Patent Office, the disclosures of which are incorporated herein by reference in their entirety.

BACKGROUND

1. Field of the Invention

The present invention relates to a cooling device and a cooling system for cooling a data center comprising a plurality of computer servers, and in addition, to an auxiliary cooling device for cooling the data center in case a main cooling device cannot be used to cool the data center.

2. Discussion of the Related Art

A computer server comprises a plurality of exothermic electronic components arranged on a printed-circuit board, and those electronic components produce heat as a result of being energized to carry out data processing. Therefore, a temperature in a datacenter in which a plurality of servers is installed is raised by the heat of the electronic components. The temperature in the datacenter thus raised is conventionally lowered using an air conditioner thereby cooling the heated electronic components of the servers. In addition, the electronic components itself are cooled directly or indirectly by a refrigerant such as water, brine, etc. cooled by a chiller unit. However, since the data processing of the electronic components is carried out ceaselessly, the chiller unit has to be operated ceaselessly too. Therefore, electric consumption of the air conditioner, and a load on the chiller unit for cooling the refrigerant are increased according to an increase in an amount of the heat generated by the electronic components. As a result, a running cost of the data center increases. In order to avoid such an increase in the running cost of the data center, it is necessary to downsize the cooling system of the data center.

In addition, a backup cooling system composed mainly of a chiller unit is used in the prior art for the purpose of cooling the data center in case the air conditioner or a main chiller unit is out of order, or in case of a power outage. The backup cooling system of this kind is configured to prepare cool water by the chiller unit, and the prepared cool water is reserved in the backup cooling system to be used for cooling the data center in case of aforementioned emergency situation. Specifically, the cool water of 5 to 8 degrees is reserved in the backup cooling system in an amount sufficient to cool the data center for about six hours. Thus, the conventional backup cooling system has to be large enough to continuously contain such a large amount of water. In addition to the above-explained disadvantage, a large electricity cost is required to operate the chiller unit continuously. Therefore, it is necessary to downsize the conventional backup cooling system, and reduce the cost of running the system.

For example, an energy-saving cold storage comprising an ice making pit arranged underneath the storage is disclosed in Japanese Patent Laid-Open No. 60-207877. According to the teachings of Japanese Patent Laid-Open No. 60-207877, the ice making pit is configured to freeze water reserved therein in winter time by dissipating heat of the water to the atmosphere using a heat pipe penetrating through the storage. Therefore, an inner space of the storage can be cooled by cold energy of the ice without running cost.

Japanese Patent Laid-Open No. 2002-372354 discloses a cooling system capable of saving on power consumption and cost. According to the teachings of Japanese Patent Laid-Open No. 2002-372354, a refrigerator is driven during nighttime thereby storing ice in a storage tank utilizing cheaper nighttime electricity. The cold energy of the ice thus prepared during the nighttime is utilized during the daytime by circulating cold water melted from the ice within a cold water showcase. Further, a coil is arranged around the cold water showcase and refrigerant is circulated through the coil. Therefore, the cold water showcase serves as an evaporator for the refrigerator.

In addition, Japan Patent Laid-Open No. 11-223449 discloses a cooling system comprising: a chiller unit for cooling brine to prepare ice: a heat exchanger for exchanging heat between the cooling system and the chiller unit; and an ice storage tank. According to the teachings of Japanese Patent Laid-Open No. 11-223449, the cooling system is connected with both of the heat exchanger and the chiller unit. The ice in the storage tank can be used to keep the cooling system at a low temperature in the form of cool water. Therefore, the cooling system taught by Japanese Patent Laid-Open No. 11-223449 can be kept at a low temperature not only by the chiller unit but also by the cold energy of the ice. In addition, it is also possible to cool down the cooling system using both of the chiller unit and the ice in the storage tank. According to the teachings of Japanese Patent Laid-Open No. 11-223449, the chiller unit is also operated to prepare the ice during the nighttime utilizing cheaper nighttime electricity.

Further, Japanese Patent Laid-Open No. 7-4800 discloses a heat pipe type supercooling ice making equipment comprising: a heat pipe; a jacket for circulating refrigerant from a refrigerator arranged on an upper part of the heat pipe; a heater arranged on a lower part of the heat pipe; a coil-shaped resin tube for letting water therethrough which is wound around the heat pipe; an ice heat storage device (i.e., a tank); and a supercooled water destructing plate to which the water discharged from the tube is dropped. According to the teachings of Japanese Patent Laid-Open No. 7-4800, the water is circulated between the tube and the ice heat storage device while driving the refrigerator using nighttime electricity. Consequently, the heat pipe is activated as a heat exchanger, and the water flowing through the tube is supercooled. The water thus supercooled is discharged from the tube and collide against the supercooled water destructing plate and is frozen.

However, according to the cold storage taught by Japanese Patent Laid-Open No. 60-207877, cold energy of the ice in the ice making pit may be radiated to the atmosphere through the soil around the ice making pit when the external temperature is higher than a coagulation temperature.

Meanwhile, according to the teachings of Japanese Patent Laid-Open No. 2002-372354 and No. 11-223449, the chiller unit is the only cooling means storing the cold energy. Therefore, in case the chiller unit has some kind of trouble or in case of power outage, the cooling systems taught by Japanese Patent Laid-Open No. 2002-372354 and No. 11-223449 are unable to perform their cooling function.

Also, the ice making equipment taught by Japanese Patent Laid-Open No. 7-4800 cannot make ice in case the refrigerator is in trouble or in case of power outage. In addition to the above-explained disadvantage, according to the teachings of Japanese Patent Laid-Open No. 7-4800, the cold energy in the ice heat storage device cannot be transported in case the water therein is completely frozen.

SUMMARY

The present invention has been conceived noting above-mentioned problems, and it is therefore an object of the present invention to provide a cooling system for cooling a data center which is capable of reducing a running cost for cooling an exothermic electronic component of a computer server. In addition, another object of the present invention is to provide an auxiliary cooling device for cooling the exothermic electronic component in case the cooling device is not available to cool the exothermic electronic component.

In order to achieve the aforementioned objective, according to a first example of the present invention, there is provided a cooling system for a data center, in which a plurality of servers having exothermic electronic components is installed in a housing, comprising: a circuit, in which a cooling medium is circulated therethrough; a main cooling device, which is connected with the electronic components through the circuit, and to which the cooling medium heated by drawing heat from the electronic components is returned; and an auxiliary cooling device, which is arranged on a return pipe of the circuit between the main cooling device and the electronic components to assist the main cooling device in cooling the cooling medium.

The auxiliary cooling device comprises a tank which stores the cooling medium therein, and a plurality of heat pipes which is adapted to cool or freeze the cooling medium by radiating heat of the cooling medium to the atmosphere. For example, the heat pipe is a thermosiphon, in which a volatile and condensable working fluid is encapsulated air-tightly, and a direction to transport the heat is restricted unilaterally by allowing condensed working fluid to drop only gravitationally. Specifically, one of end portions of the thermosiphon is immersed into the cooling medium in the tank to serve as an evaporating portion, and other end portion of the thermosiphon is exposed to the atmosphere to serve as a condensing portion.

The cooling system according to the first example further comprises a heat exchanger, which is arranged on the circuit between the electronic components and the cooling devices to exchange the heat of the electronic components and cold energy of the cooling medium.

The cooling system further comprises a cooling tower, which is connected with the main cooling device to radiate heat of the main cooling device to the atmosphere.

In addition, the auxiliary cooling device further comprises a flow channel letting through the cooling medium supplied to the tank unilaterally.

According to the second example of the present invention, the cooling system further comprises a mixing tank, to which the cooling medium heated by the electronic component, and the cooling medium cooled by the main cooling device or the auxiliary cooling device, are supplied to regulate the temperature thereof. The cooling medium mixed in the mixing tank is selectively supplied to the main cooling device and the auxiliary cooling device to be cooled, and also used to cool the electronic component.

The mixing tank is divided into a plurality of mixing chambers, and the adjoining mixing chambers are connected by a through hole. Specifically, the cooling medium heated by the electronic component is supplied to one of the mixing chambers connected with the electronic component, and the cooling medium cooled by the main cooling device or the auxiliary cooling device is supplied to another one of the mixing chambers connected with the main cooling device and the auxiliary cooling device. Therefore, the cooling medium heated by the electronic component, and the cooling medium cooled by the main cooling device or the auxiliary cooling device are mixed gradually in the mixing tank while flowing across the mixing chambers.

According to the second example, the cooling system further comprises, a first switching valve, which switches a route for feeding the cooling medium from the mixing tank to the electronic component between a route from said one of the mixing chamber to the electronic component, and a route from said another one of the mixing chamber to the electronic component; a first pump, which is arranged between the first switching valve and the electronic component to feed the cooling medium to the electronic component; a second switching valve, which switches a route for feeding the cooling medium from the mixing tank to the main cooling device between a route from said one of the mixing chamber to the main cooling device, and a route from said another one of the mixing chamber to the main cooling device; a second pump, which is arranged between the second switching valve and the main cooling device to feed the cooling medium to the main cooling device; and a third pump, which is arranged on a route between said one of the mixing chamber and the auxiliary cooling device to feed the cooling medium in said one of the mixing chamber to the auxiliary cooling device.

According to the third example of the present invention, the cooling system of the first example further comprises: a first switching valve, which returns the cooling medium heated by the heat from the electronic components selectively to the main cooling device and the auxiliary cooling device; and a second switching valve, which supplies the cooling medium to the electronic component selectively from the main cooling device and the auxiliary cooling device.

The cooling system according to the third example further comprises: a first pump, which is arranged on the circuit connecting the electronic component and the heat exchanger to circulate the cooling medium therethrough; a second pump, which is arranged on the circuit connecting the heat exchanger and the main cooling device to circulate the cooling medium therethrough; and a third pump, which is arranged on the circuit connecting the main cooling device and the cooling tower to circulate the cooling medium therethrough.

According to the fourth example, the auxiliary cooling device further comprises a heat insulating layer, which covers the tank to prevent the tank from being warmed by an external heat.

In addition, according to the fourth example, the auxiliary cooling device further comprises: a cold storage medium, which is sealed in the tank to be frozen by external cold energy entering into the tank through the thermosiphon; and a heat exchanging tube, which is arranged around the evaporating portion of the thermosiphon, and through which the cold energy of the frozen cold storage medium in the tank is transferred to the cooling medium flowing therethrough.

Specifically, the heat insulating layer comprises: an inner layer formed of an evacuated panel in which an internal pressure is reduced to be lower than an atmospheric pressure; and an outer layer formed of heat insulating porous material.

The aforementioned heat exchanging tube includes a coil heat exchanger formed by winding a hollow tube around the evaporating portion of the thermosiphon; and material of the heat exchanging tube is selected from the group consisting of copper, copper alloy, aluminum, aluminum alloy, and synthetic resin.

According to a fifth example of the present invention, the auxiliary cooling device further comprises: a soil layer containing predetermined moisture and covering the tank; and another heat pipe which is buried in the soil layer at least partially to freeze the moisture in the soil layer by radiating the heat of the moisture unilaterally to the atmosphere, under the condition in which a temperature of the moisture in the soil layer is higher than an external temperature and the external temperature is lower than a predetermined temperature.

The aforementioned another heat pipe is also a thermosiphon, in which a volatile and condensable working fluid is encapsulated air-tightly, and a direction to transport the heat is restricted unilaterally by allowing the condensed working fluid to drop only gravitationally. Specifically, one of end portions of the thermosiphon buried in the soil layer serves as an evaporating portion; and other end portion of the thermosiphon exposed to the atmosphere serves as a condensing portion.

Specifically, a thickness of the soil layer is approximately 1 meter, and material of the soil layer is selected from a group consisting of sand, loam and clay. For example, in case the soil layer is formed of sand, a moisture content of the soil layer is kept within a range of 2.5 to 10%, in case the soil layer is formed of loam, a moisture content of the soil layer is kept within a range of 10 to 17.5%, and in case the soil layer is formed of clay, a moisture content of the soil layer is kept within a range of 17.5 to 25%.

In addition, the heat exchanging tube includes a U-shaped heat exchanger formed by bending a hollow tube into U-shape and arranged in the vicinity of the evaporating portion of the thermosiphon.

According to the sixth example of the present invention, the cooling system further comprises: an air conditioner, which is arranged in the housing to control the temperature in the housing thereby cooling the server; and an assist heat pipe, which transports heat in the housing unilaterally to the atmosphere thereby assisting the air conditioner. The assist heat pipe is also a thermosiphon, in which a volatile and condensable working fluid is encapsulated air-tightly, and in which a direction to transport the heat is restricted unilaterally by allowing the condensed working fluid to drop only gravitationally. Specifically, one of end portions of the thermosiphon is situated in the housing above the server in a direction of gravitational force, and the other end portion of the thermosiphon is exposed to the atmosphere.

In addition, the auxiliary cooling device is buried in the ground in a cold region where a freezing index is higher than 400 degree C.·day.

Thus, according to the cooling device of the first example, the auxiliary cooling device is arranged on the pipeline returning the cooling medium from the electronic component to the main cooling device. Therefore, the cooling medium heated as a result of cooling the electronic components is cooled prior to reaching the main cooling device. The cooling medium thus cooled by the auxiliary cooling device is then supplied to the main cooling device. As a result, a burden of the main cooling device can be lightened so that the main cooling device can be downsized and the running cost thereof can be reduced. In case the temperature of the cooling medium circulating in the circuit is lowered to a desired temperature, the main cooling device can be stopped. In addition to the above-explained advantages, since the auxiliary cooling device is configured to radiate the heat of the cooling medium using the heat pipe, maintenance and repair of the auxiliary cooling device is substantially unnecessary.

In the auxiliary cooling device, the heat of the cooling medium in the tank is radiated to the atmosphere through the heat pipe. As described, the thermosiphon is used as the heat pipe, and the direction of the thermosiphon to transport the heat is restricted to one direction by thermal diode characteristics thereof. Therefore, an external heat cannot enter into the auxiliary cooling device through the thermosiphon, that is, the cooling medium will not be warmed by the external heat.

As described, the cooling system of the present invention comprises the heat exchanger between the server and the cooling devices. Therefore, the heat of the electronic component and the cold energy of the main cooling device can be exchanged in the heat exchanger so that the cooling medium heated by the electronic component can be cooled prior to reaching the auxiliary cooling device.

Since the main cooling device is connected with the cooling tower, the heat of the cooling medium returned to the main cooling device can be radiated to the atmosphere from the cooling tower.

As described, according to the second example, the flow channel for letting through the cooling medium unilaterally is formed in the auxiliary cooling device. Therefore, the cooling medium can be cooled by the thermosiphon when flowing through the auxiliary cooling device.

According to the second example of the present invention, the cooling medium heated by the electronic component, and the cooling medium cooled by the main and the auxiliary cooling devices are supplied to the mixing tank. Therefore, those cooling mediums are mixed together in the mixing tank, and as a result, the temperature of the cooling medium is first neutralized in the mixing tank. The cooling medium thus neutralized in the mixing tank can be supplied selectively to the main cooling device and the auxiliary cooling device to be cooled. For this reason, a burden on the main cooling device can be lightened and cold energy in the ice storage device can be prevented from being consumed wastefully. Moreover, in case the cooling medium can be cooled sufficiently in the mixing tank, the cooling medium can also be supplied to the electronic component directly from the mixing chamber. In this case, the electronic components can be cooled by the cooling medium cooled only in the mixing tank without running the main cooling device.

As described, the mixing tank is divided into a plurality of mixing chambers, and adjoining chambers are communicated through a through hole. Specifically, the cooling medium heated by the electronic component is supplied to one of the mixing chambers connected with the electronic component, and the cooling medium cooled by the main cooling device or the auxiliary cooling device is supplied to another one of the mixing chambers connected with the main cooling device and the auxiliary cooling device. The cooling medium supplied to said one of the mixing chamber is convectively migrated toward said another one of the mixing chamber through the through holes, and the cooling medium supplied to said another one of the mixing chamber is convectively migrated toward said one of the mixing chamber through the through holes. Therefore, the cooling medium of high temperature and the cooling medium of low temperature can be mixed stepwise while flowing across the mixing chambers.

In addition to the above explained advantages, according to the cooling system of the second example, the cooling medium can be supplied to the electronic component selectively from said one of the mixing chamber and said another one of the mixing chambers depending on the situation by switching the first switching valve. Therefore, the electronic component can be prevented from being cooled insufficiently or excessively. Likewise, the cooling medium can be supplied to the main cooling device selectively from said one of the mixing chamber and said another one of the mixing chambers depending on the situation by switching the second switching mechanism. Therefore, a burden on the main cooling device can be lightened.

According to the cooling system of the third example, the cooling medium heated by the heat of the electronic component can be returned selectively to the main cooling device and to the auxiliary cooling device by switching the first switching mechanism, and the cooling medium cooled in the main cooling device and the auxiliary cooling device can be selectively used to cool the electronic component by switching the second switching mechanism. Therefore, the cold energy stored in the auxiliary cooling device can be used to cool the electronic component even if the main cooling device is not available.

In addition to the above-explained advantages, according to the third example, the cooling medium can be forced to circulate by the first pump in the circuit connecting the electronic component and the heat exchanger, by the second pump in the circuit connecting the heat exchanger and the main cooling device, and by the third pump in the circuit connecting the main cooling device and the cooling tower.

According to the fourth example, the tank of the auxiliary cooling device is covered by the heat insulating layer. Therefore, the cold energy stored in the auxiliary cooling device can be prevented from being wasted by the external heat around the tank so that the cold energy stored therein can be maintained over long periods.

Further, according the fourth example, the cold storage medium is sealed in the tank of the auxiliary cooling device instead of the cooling medium in a manner not to circulate in the cooling system, and in a manner to be frozen by the external cold energy entering into the tank through the thermosiphon. In addition, the heat exchanging tube is formed around the thermosiphon. Therefore, the cold energy of the frozen cold storage medium can be transferred easily to the liquid phase cooling medium flowing through the heat exchanging tube.

As described, the heat insulating layer comprises the inner layer formed of an evacuated panel in which an internal pressure is reduced to be lower than an atmospheric pressure, and the outer layer formed of heat insulating porous material. Therefore, heat insulating properties of the heat insulating layer can be enhanced.

Specifically, the heat exchanging tube is formed by winding the hollow tube around the thermosiphon. That is, a length of a portion of the heat exchanging tube where the heat exchange between the frozen cold storage medium and the liquid phase cooling medium takes place can be elongated. In case of forming the heat exchanging tube using any of copper, copper alloy, aluminum, aluminum alloy, heat conductivity thereof can be improved. Alternatively, In case of forming the heat exchanging tube using synthetic resin, a cost of the material can be reduced.

According to the fifth example, the soil layer is frozen by another heat pipe under the condition in which the temperature of the moisture contained in the soil layer is higher than the external temperature, and the external temperature is lower than a predetermined operating temperature of said another heat pipe. In this case, therefore, cold storage property of the auxiliary cooling device can be further enhanced.

In addition, according to the fifth example, the thermosiphon is also used as said another heat pipe buried in the soil layer. Therefore, the external heat cannot enter into the soil layer through the thermosiphon so that the frozen moisture of the soil layer can be prevented from being melted by the external heat.

Specifically, the soil layer is formed to have a sufficient thickness to maintain the cold energy in the auxiliary cooling device all through the year even during summer, e.g., to have approximately 1 meter thickness. Therefore, a permafrost layer can be formed around the tank of the auxiliary cooling device by freezing the soil layer. The cold energy of the permafrost layer can be utilized to cool the electronic component by arranging the heat exchanger around the thermosiphon buried in the soil layer.

In addition, a configuration of the heat exchanging tube can be simplified by shaping the heat exchanging tube into a U-shape. In this case, a length of the heat exchanging tube can be shortened.

According to the sixth example, the assist heat pipe is arranged in the housing to radiate the heat in the housing to the atmosphere. Therefore, if the air conditioner is arranged in the housing, a burden of the air conditioner can be lightened. As a result, an electric consumption and CO₂ emission of the air conditioner can be reduced. Specifically, one of the end portions of the assist heat pipe is situated above the servers, and the other end portion of the assist heat pipe is exposed to the atmosphere. Therefore, in addition to the above-explained advantage, the heat of the servers in the housing can be radiated efficiently to the atmosphere through the assist heat pipe.

According to the present invention, the auxiliary cooling device is applied to a data center located in the cold region where a freezing index is higher than 400 degree C.·day. Therefore, cooling efficiency of the thermosiphon can be improved so that the cooling medium or the cold storage medium stored in the tank of the auxiliary cooling device can be frozen.

Thus, according to the present invention, the auxiliary cooling device is configured to store the cold energy by radiating the heat of the cooling medium or the cold storage medium stored therein to the atmosphere through the heat pipe thereby freezing the cooling medium or the cold storage medium, under the condition in which the temperature of the cooling medium or the cold storage medium is higher than an external temperature and the external temperature is lower than a predetermined temperature. Therefore, the auxiliary cooling device is capable of storing the cold energy therein without consuming electricity, that is, free of cost. In addition, the auxiliary cooling device is capable of storing the cold energy without emitting greenhouse gas such as CO₂. This means that the datacenter using the auxiliary cooling device of the present invention will not harm the environment. Moreover, the auxiliary cooling device is configured to store the cold energy by freezing the cooling medium or the cold storage medium stored therein. Therefore, in addition to the above-explained advantages, a capacity of the auxiliary cooling device for storing the cold energy with respect to an instillation area is larger than a cold storage device using a liquid phase cooling medium. For this reason, the auxiliary cooling device can be downsized so that a construction cost and an installation area thereof can be reduced. That is, even if a conventional cold storage device has already been used in a cooling system for a datacenter, the conventional cold storage device can be replaced easily with the auxiliary cooling device of the present invention without expanding the installation area of the cooling system. In addition, a capacity of the auxiliary cooling device can be increased by merely increasing the number of tanks without introducing additional air conditioner or chiller units.

BRIEF DESCRIPTION OF THE DRAWINGS

Features, aspects, and advantages of exemplary embodiments of the present invention will become better understood with reference to the following description and accompanying drawings, which should not be read to limit the invention in any way.

FIG. 1 is a schematic view showing an exemplary structure of the cooling system for a datacenter according to the first example of the present invention;

FIG. 2 is a schematic view showing an exemplary structure of the cooling system for a datacenter according to the second example of the present invention;

FIG. 3 is a schematic view showing an exemplary structure of the cooling system for a datacenter according to the third example of the present invention;

FIG. 4 is a schematic view showing an exemplary structure of the cooling system for a datacenter according to the fourth example of the present invention;

FIG. 5 is a schematic view showing an installation example of the cooling system for a datacenter shown in FIG. 4;

FIG. 6 is a schematic view showing an outlook of the auxiliary cooling device used in the cooling system shown in FIG. 4;

FIG. 7 is a sectional view showing a longitudinal section of the auxiliary cooling device shown in FIG. 6;

FIG. 8 is a close-up showing the cross section shown in FIG. 7 partially in an enlarged scale;

FIG. 9 is a schematic view showing an example of the heat exchanging tube used in the auxiliary cooling device shown in FIG. 6;

FIG. 10 is a schematic view showing a state in which the cooling medium around the exchanging tube shown in FIG. 9 is frozen;

FIG. 11 is a schematic view showing an exemplary structure of the cooling system for a datacenter according to the fifth example of the present invention;

FIG. 12 is a schematic view showing an outlook of the auxiliary cooling device used in the cooling system for a data center shown in FIG. 11;

FIG. 13 is a sectional view showing a longitudinal section of the auxiliary cooling device shown in FIG. 12;

FIG. 14 is a sectional view showing a cross section of the auxiliary cooling device shown in FIG. 12;

FIG. 15 is a schematic view showing a configuration of the thermosiphon type heat pipe arranged in the soil layer;

FIG. 16 is a schematic view showing a modification of the auxiliary cooling device shown in FIGS. 12, 13 and 14;

FIG. 17 is a schematic view showing another modification of the auxiliary cooling device shown in FIGS. 12, 13 and 14;

FIG. 18 is a sectional view showing a cross section of the auxiliary cooling device shown in FIG. 17; and

FIG. 19 is a schematic view showing an example of arranging the assist heat pipe of the sixth example in the housing.

DETAILED DESCRIPTION

Hereinafter, exemplary embodiments of the present invention will be explained with reference to the accompanying drawings. FIG. 1 is a schematic view showing an exemplary structure of the cooling system for a datacenter according to the first example. In the datacenter 1, the plurality of server racks 3 housing the computer servers is installed in a housing 2. In this example, any kind of appropriate building can be used as the housing 2. Each of the servers comprises a plurality of electronic components 8 arranged on a printed-circuit board, and those electronic components 8 produce heat as a result of being energized to carry out data processing. For example, the electronic component 8 includes a central processing unit (abbreviated as CPU), a memory device, an electric power source and so on. Those electronic components 8 are contacted individually with a cold plate 9 to exchange the heat therebetween. Therefore, the electronic components 8 are cooled directly by the cold plates 9.

Specifically, the cold plate 9 is a hollow metal plate, and the cooling medium is allowed to flow through the hollow space. In order to transfer an external heat to the cooling medium flowing through the hollow portion of the cold plate 9, the cold plate 9 is preferably made of material having good heat conductivity. Therefore, according to the first example, the cold plate 9 is made of copper or copper alloy. The cold plate 9 is connected with a heat exchanger 10 through pipelines forming a cooling circuit C1. Therefore, the heat of the cold plate 9 can be transported to the heat exchanger 10 by the cooling medium circulating in the cooling circuit C1.

The heat exchanger 10 is configured to exchange heat between high temperature cooling medium flowing therethrough and low temperature cooling medium flowing therethrough, and for example, a plate type heat exchanger or the like can be used as the heat exchanger 10. In order to transport the heat, the cooling medium is selected from water, water solution containing predetermined amount of anticorrosion additive, ethylene glycol based or calcium chloride based brine whose freezing point is lower than 0 degrees C. (i.e., antifreeze liquid), hydrochlorofluorocarbon such as R-134 or the like.

The temperature of the cooling medium in the cooling circuit C1 is raised as a result of drawing the heat from the electronic component 8, and the cooling medium thus heated by the heat of electronic component 8 is flown from the cold plate 9 toward the heat exchanger 10. In the heat exchanger 10, the heat of the cooling medium in the circuit C1 is transferred to low temperature cooling medium circulating in an after-mentioned auxiliary cooling circuit C2. The cooling medium in the cooling circuit C1 thus cooled in the heat exchanger 10 is returned to the cold plate 9 to cool the electronic component 8.

The heat exchanger 10 is also connected with a chiller unit 11 functioning as a main cooling device through pipelines forming the auxiliary cooling circuit C2. Therefore, the heat of the cooling medium circulating in the cooling circuit C1 can be transported from the heat exchanger 10 to the chiller unit 11 by the cooling medium circulating in the auxiliary cooling circuit C2. Specifically, the chiller unit 11 is a heat pump comprising: an internal circuit in which cooling medium such as hydrochlorofluorocarbon circulates therethrough; a compressor 12 which compress the cooling medium by applying a pressure to the cooling medium; a condenser 13 which transports heat of the compressed cooling medium to outside thereby condensing the cooling medium; an expansion valve 14 which expands the condensed cooling medium thereby lowering the temperature of the cooling medium; and an evaporator 15 at which external heat is conducted to the condensed cooling medium. Thus, the chiller unit 11 is configured to transport the heat in the form of latent heat by compressing and expanding the cooling medium circulating therein. For example, a conventional turbo refrigerator and a screw type chiller using hydrochlorofluorocarbon as the cooling medium, an absorption refrigerator using water as the cooling medium and so on can be used as the chiller unit 11.

A temperature of the cooling medium circulating in the auxiliary cooling circuit C2 is raised in the heat exchanger 10 as a result of receiving the heat of the cooling medium circulating in the cooling circuit C1. Then, the cooling medium in the auxiliary cooling circuit C2 thus warmed in the heat exchanger 10 is flown toward the chiller unit 11 via an after-mentioned auxiliary cooling device 18, and the heat thereof is absorbed at the evaporator 15 by the cooling medium circulating in the internal circuit of chiller unit 11. The cooling medium in the auxiliary circuit C2 thus cooled in the chiller unit 11 is then returned to the heat exchanger 10, and the cold energy thereof is transferred to the cooling medium in the cooling circuit C1. Consequently, the electronic component 8 is cooled by the cold energy of the cooling medium circulating in the cooling circuit C1 through the cold plate 9.

The condenser 13 of the chiller unit 11 is connected with a cooling tower 16 erected outside of the cooling system through pipelines forming a radiating circuit C3, and cooling water is circulated in the radiating circuit C3. Therefore, the heat of the cooling medium circulating in the internal circuit of the chiller unit 11 is transmitted to the cooling water circulating in the radiating circuit C3 at the condenser 13. The heat thus transmitted to the cooling water in the radiating circuit C3 is radiated from the cooling tower 16 to the atmosphere by a fan 17.

In order to cool the cooling medium warmed in the heat exchanger 10 prior to arriving at the chiller unit 11, the auxiliary cooling device 18 is arranged in the auxiliary cooling circuit C2 on the route from the heat exchanger 10 to the chiller unit 11. For this purpose, the auxiliary cooling device 18 is provided with: a tank 19 which reserves the cooling medium therein temporarily; and a plurality of heat pipes 20 which radiate the heat of the cooling medium in the tank 19 to the atmosphere.

Specifically, the tank 19 is a watertight hollow container. Therefore, the water outside of the tank will not penetrate into the tank 19 and the cooling medium in the tank 19 will not leak from the tank 19. As described, a role of the tank 19 is to reserve the cooling medium temporarily thereby cooling the cooling medium in advance of reaching the chiller unit 11. Therefore, the tank 19 is preferably insulated from the external heat. For this reason, the tank 19 is formed of low-heat conductive material such as concrete. In order to protect the tank 19 from the external heat, it is preferable to bury the tank 19 in the ground.

In addition, a plurality of flow channels 21 is formed on a bottom of the tank 19. More specifically, the flow channel 21 is a grove between ribs 22 for letting through the cooling medium. Therefore, in the auxiliary cooling device 18, the cooling medium flowing from the heat exchanger 10 is allowed to flow through the flow channels 21 unidirectionally toward the chiller unit 11. In each of the flow channel 21, the heat pipes 20 are erected substantially vertically at predetermined intervals. Specifically, one of end portions of the heat pipe 20 immersed into the cooling medium in the tank 19 serves as an evaporating portion 20 a at which working fluid encapsulated therein is evaporated. The other end portion of the heat pipe 20 is exposed to the outside of the tank 19 to be contacted with the external air. That is, the other end portion 20 b serves as a condensing portion at which the vaporized working fluid in the heat pipe 20 is condensed by radiating the heat of the vaporized working fluid to the atmosphere. For this purpose, a plurality of radiating fins 23 is arranged on the condensing portion 20 b.

Specifically, the heat pipe 20 is a thermosiphon comprising an evacuated hollow container, and volatile and condensable working fluid contained in the container air-tightly. In order to exchange internal heat and external cold energy efficiently, the container of the heat pipe 20 is preferably made of material having good heat conductivity such as copper. Preferably, the heat pipe 20 is configured to be activated under the condition where the external temperature is lower than 10 degrees C. For this purpose, the working fluid of the heat pipe 20 is selected from ammonia and hydrochlorofluorocarbon such as R-134 or the like whose boiling point is lower than 10 degrees C., and 20 to 30 volume percent of the working fluid is contained in the heat pipe 20.

Therefore, provided that the external temperature is lower than 10 degrees C., and the temperature of the cooling medium in the tank 19 is higher than 10 degrees C., the working fluid is vaporized in the evaporating portion 20 a. The vapor of the working fluid rises toward the condensing portion 20 b where the temperature and the pressure are lower than those in the evaporating portion 20 a, and the heat in the tank 19 thus transported to the condensing portion 20 b by the vaporized working fluid is then radiated to the atmosphere thorough the fins 23. As a result, the cooling medium in the tank 19 is cooled and the temperature thereof is lowered. The vaporized working fluid is condensed again in the condensing portion 20 b and returned gravitationally to the evaporating portion 20 a. Thus, a thermal diode characteristic of the heat pipe 20 ensures to transport the heat unilaterally from evaporating portion 20 a toward the condensing portion 20 b thereby radiating the heat of the cooling medium in the tank 19 unilaterally to the outside of the tank 19. Conversely, in case the external temperature is higher than 10 degrees C., the heat pipe 20 will not be activated. In this case, therefore, the external temperature is prevented from entering into the tank 19 so that the temperature of the cooling medium in the tank 19 will not be raised by the external temperature.

Additionally, it is possible to arrange a wick in the evaporating portion 20 a of the heat pipe 20 from a level of the cooling medium in the tank 19 to a bottom of the heat pipe 20. In this case, the liquid phase working fluid in the evaporating portion 20 a is soaked up to an upper end of the wick by capillary action of the wick. Therefore, the portion of the heat pipe 20 in which the wick is thus arranged is allowed to serve as the evaporating portion 20 a entirely even if a level of the liquid phase working fluid in the evaporating portion 20 a becomes lower than the level of the cooling medium in the tank 19. However, the thermal diode characteristics of the heat pipe 20, that is, the direction to transport the heat will not be changed even if the wick is thus arranged in the evaporating portion 20 a.

Thus, according to the first example, the heat of the electronic component 8 is drawn by the cooling medium circulating in the cooling circuit C1. The heat of the electronic component 8 transmitted to the cooling medium circulating in the cooling circuit C1 is then transported to the heat exchanger 10, and transferred to the cooling medium circulating in the auxiliary cooling circuit C2 cooled by the chiller unit 11. The cooling medium in the cooling circuit C1 thus cooled in the heat exchanger 10 is returned toward the electronic component 8. Meanwhile, the cooling medium in the auxiliary cooling circuit C2 warmed in the heat exchanger 10 by the cooling medium in the cooling circuit C1 is returned to the chiller unit 11 while being cooled by the auxiliary cooling device 18 on the way.

Specifically, the heat of the cooling medium in the auxiliary cooling circuit C2 being returned from the heat exchanger 10 to the chiller unit 11 is dissipated to the atmosphere in advance through the heat pipes 20 in the auxiliary cooling device 18. That is, the cooling medium in the auxiliary cooling circuit C2 is cooled by the auxiliary cooling device 18 prior to cooling by the chiller unit 11. Therefore, the temperature of the cooling medium in the auxiliary cooling circuit C2 returned to the chiller unit 11 has already been lowered to a certain level so that the burden on the chiller unit 11 can be lightened, in comparison with a case in which the cooling medium is returned directly to the chiller unit 11 without passing through the auxiliary cooling device 18. For this reason, a running cost of the chiller unit 11 and CO₂ emission from the chiller unit 11 can be reduced, and in addition, the chiller unit 11 can be downsized.

When the temperature of the cooling medium being returned from the heat exchanger 10 to the chiller unit 11 is lowered to a desired temperature, e.g., below 10 degrees C., the chiller unit 11 can be stopped. In this case, the cooling medium circulating in the auxiliary cooling circuit C2 can be cooled sufficiently by merely radiating the heat thereof through the heat pipes 20 in the auxiliary cooling device 18, and the electronic component 8 can be cooled by the cooling medium in the cooling circuit C1 cooled by the cooling medium in the auxiliary cooling circuit C2. In this case, therefore, the running cost of the chiller unit 11 can be eliminated and CO₂ will not be emitted from the chiller unit 11. In addition, the auxiliary cooling device 18 is thus configured to cool the cooling medium without using mechanical devices such as the condenser 13 and the compressor 12 used in the chiller unit 11. Therefore, the structure of the auxiliary cooling device 18 is very simple so that maintenance of the auxiliary cooling device 18 is substantially unnecessary. Here, in order to circulate the cooling medium compulsory in the circuits C1, C2 and C3, a pump may be arranged on each of the circuits C1, C2 and C3. In addition, the servers can also be connected directly with the auxiliary cooling unit 18 and the chiller unit 11 without interposing the heat exchanger 10 therebetween.

Here will be explained the second example of the present invention with reference to FIG. 2. According to the second example, the server racks 3 are also installed in the housing 2 of the datacenter 1, and the cold plate 9 is contacted with the electronic component 8. The cold plate 9 is also connected with the heat exchanger 10 through the pipelines forming a circuit between the heat exchanger 10 and the electronic component 8, and the cooling medium is circulated in the circuit. According to the second example, in order to absorb or to buffer a volume change in the cooling medium, an expansion tank 24 is arranged on the pipeline for returning the cooling medium from the cold plate 9 to the heat exchanger 10. Therefore, the cooling medium expanded by the heat of the electronic component 8 can be temporarily reserved in the expansion tank 24. Although not especially shown in FIG. 2, the expansion tank 24 is preferably connected with the circuit through an appropriate relief valve. In addition, in order to circulate the cooling medium compulsory in the circuit, a pump 25 is arranged between the expansion tank 24 and the heat exchanger 10. Here, a conventional pump can be used as the pump 25.

The heat exchanger 10 is connected with a mixing tank 26 through a pipe line. Specifically, the mixing tank 26 is configured to regulate the temperature of the cooling medium therein stepwise by mixing hot cooling medium and cold cooling medium supplied thereto from both sides. For this purpose, according to the third example, the mixing tank 26 is divided into six mixing chambers 26 a to 26 f. The adjoining mixing chambers are connected via through holes 28 formed alternately in vertical direction. For example, the through hole 28 connecting the mixing chambers 26 a and 26 b is formed in a lower side of the mixing tank 26, and the through hole 28 connecting the mixing chambers 26 b and 26 c is formed in an upper side of the mixing chamber 26.

Specifically, the mixing chamber 26 a is connected with the heat exchanger 10 through a pipeline, and the cooling medium heated in the heat exchanger 10 is supplied to the mixing chamber 26 a. Meanwhile, the mixing chamber 26 f is connected with the chiller unit 11 functioning as the main cooling device and with an ice storage device 27 functioning as the auxiliary cooling device through pipelines. Therefore, the cooling mediums cooled by the chiller unit 11 and the ice storage device 27 are supplied to the mixing chamber 26 f. The mixing chamber 26 a is also connected with the ice storage device 27 and with the chiller unit 11 through pipelines. Therefore, the cooling medium is supplied to the chiller unit 11 selectively from the mixing chambers 26 a and 26 f. The cooling medium cooled in the chiller unit 11 is returned to the mixing chamber 26 f.

In addition, the mixing chamber 26 a is also connected with the heat exchanger 10 through a pipeline, and the mixing chamber 26 f is also connected with the heat exchange 10 through another pipeline. Therefore, the cooling medium whose temperature is regulated stepwise in the mixing chambers 26 a to 26 f is supplied to the heat exchanger 10 selectively from the mixing chambers 26 a and 26 f.

Next, a function of the mixing chamber 26 will be explained hereinafter. As described, the cooling medium heated in the heat exchanger 10 is supplied to the mixing chamber 26 a, and flows toward the mixing chamber 26 f via the mixing chambers 26 b, 26 c, 26 d and 26 e. Conversely, the cooling mediums cooled by the chiller unit 11 and the ice storage device 27 are supplied to the mixing chamber 26 f, and flows toward the mixing chamber 26 a via the mixing chambers 26 e, 26 d, 26 c and 26 b. Therefore the cooling medium having higher temperature supplied to the mixing chamber 26 a from the heat exchanger 10 is mixed with the cooling medium having lower temperature flowing from the mixing chamber 26 f. As a result, the cooled cooling medium is convectively submerged toward the lower side of the mixing chamber 26 a, and warmed cooling medium is convectively raised toward the upper side of the mixing chamber 26 a. Then, the cooled cooling medium thus migrates to the lower side of the mixing chamber 26 a flows into the adjoining mixing chamber 26 b through the through hole 28 formed in a lower side of a partition wall between the mixing chambers 26 a and 26 b. The cooling medium thus flowing into the mixing chamber 26 b from the mixing chamber 26 a is mixed with the cooling medium having lower temperature flowing into the mixing chamber 26 b from the mixing chamber 26 c. As a result, the warmed cooling medium is convectively raised toward the upper side of the mixing chamber 26 b, and the cooled cooling medium is convectively submerged toward the lower side of the mixing chamber 26 b. Then, the cooled cooling medium thus migrates to the upper side of the mixing chamber 26 b flows into the adjoining mixing chamber 26 c through the through hole 28 formed in an upper side of a partition wall between the mixing chambers 26 b and 26 c. Thus, the high temperature cooling medium supplied to the mixing chamber 26 a flows convectively toward the mixing chamber 26 f while being cooled gradually.

Conversely, the cooling mediums cooled in the ice storage device 27 and the chiller unit 11 are supplied to the mixing chamber 26 f as described. The cooling medium having lower temperature supplied to the mixing chamber 26 f is mixed with the cooling medium having higher temperature flowing into the mixing chamber 26 f from the mixing chamber 26 e, and the cooling medium having lower temperature is convectively submerged toward the lower side of the mixing chamber 26 f. Then, the cooling medium migrates to the lower side of the mixing chamber 26 f and flows into the adjoining mixing chamber 26 e through the through the hole 28 formed in a lower side of a partition wall between the mixing chambers 26 f and 26 e. The cooling medium thus flowing into the mixing chamber 26 e from the mixing chamber 26 f is mixed with the cooling medium having higher temperature flowing into the mixing chamber 26 e from the mixing chamber 26 d. As a result, the warmed cooling medium is convectively raised toward the upper side of the mixing chamber 26 e, and flows into the adjoining mixing chamber 26 d through the through hole 28 formed in an upper side of a partition wall between the mixing chambers 26 e and 26 d. Thus, the low temperature cooling medium supplied to the mixing chamber 26 f flows convectively toward the mixing chamber 26 a while being warmed gradually. That is, the cooling medium in the cooling chamber 26 a is at the highest temperature, and the temperature of the cooling medium is lowered gradually from the mixing chambers 26 b to 26 f.

The cooling medium whose temperature is thus regulated in the mixing chamber 26 a is partially supplied to the ice storage device 27. For this purpose, a pump 29 is arranged on the pipeline connecting the mixing chamber 26 a with the ice storage device 27. Specifically, the ice storage device 27 is configured to cool or freeze the cooling medium supplied thereto from the mixing tank 26 by radiating the heat of the cooling medium to the atmosphere. In other words, the ice storage device 27 is configured to store the cold energy by cooling or freezing the cooling medium stored therein by external cold energy. The cold energy of the ice stored in the ice storage device 27 is used to cool the cooling medium supplied thereto from the mixing chamber 26 a, and transported to the mixing chamber 26 f by the cooled liquid phase cooling medium. Therefore, in order to cool the datacenter 1 effectively, the mixing tank 26 and the ice storage device 27 are preferably installed in a cold region where a freezing index is higher than 400 degree C.·day.

Specifically, the ice storage device 27 comprises: a tank 30 which reserves the cooling medium supplied from the mixing chamber 26 a temporarily; and a heat pipe 31 which cools and freezes the cooling medium stored in the tank 30 by radiating the heat of the cooling medium to the atmosphere. The tank 30 is a watertight hollow container, therefore, the water outside of the tank 30 will not penetrate into the tank 30 and the cooling medium in the tank 30 will not leak from the tank 30. In addition, the tank 30 is preferably insulated from the external heat. Therefore, tank 30 is preferably formed of low-heat conductive material such as concrete, and buried in the ground.

The heat pipe 31 is erected substantially vertically in the tank 30, and one of the end portions of the heat pipe 31 immersed into the cooling medium in the tank 30 serves as an evaporating portion 31 a at which working fluid encapsulated therein is evaporated. The other end portion of the heat pipe 31 is exposed to outside of the tank 30 to be contacted with the atmosphere. That is, the other end portion 31 b serves as a condensing portion at which the vaporized working fluid in the heat pipe 31 is condensed by radiating the heat of the vaporized working fluid to the atmosphere. For this purpose, a plurality of radiating fins 32 are arranged on the condensing portion 31 b.

As in the first example, a thermosiphon is also used in the second example as the heat pipe 31. Therefore, a direction of the heat pipe 31 to transport the heat is restricted to one direction by the thermal diode characteristics thereof so that the external heat will not enter into the tank 30 through the heat pipe 31. The working fluid encapsulated in the heat pipe 31 is also selected from ammonia and hydrochlorofluorocarbon such as R-134 or the like whose boiling point is lower than 10 degrees C.

Therefore, the working fluid in the heat pipe 31 is vaporized in the evaporating portion 31 a under the condition where the external temperature is lower than 10 degrees C., and vapor of the working fluid rises toward the condensing portion 31 b. The heat of the cooling medium is thus transported to the condensing portion 31 b by the vaporized working fluid in the form of latent heat, and radiated to the atmosphere through the fins 32. As a result, the vaporized working fluid is condensed again and returned gravitationally to the evaporating portion 31 a. Thus, the cooling medium in the ice storage device 27 is cooled by the external cold energy under the condition where the external temperature is lower than 10 degrees C., and frozen under the condition where the external temperature becomes lower than zero. As described, the vaporized working fluid is condensed in the condensing portion 31 b and returned gravitationally to the evaporating portion 31 a. Therefore, a content of the liquid phase working fluid in the condensing portion 31 b is much smaller than that of the liquid phase working fluid in the evaporating portion 31 a. For this reason, the external heat will not be transported from the top side of the heat pipe 31, that is, from the condensing portion 31 b to the evaporating portion 31 a even if the external temperature is higher than 10 degrees C. Thus, the working fluid in the tank 30 can be prevented from being warmed by the external heat.

As described, the heat exchanger 10 is connected with the mixing chambers 26 a and 26 f through the pipelines, and a switching valve 33 is arranged at a junction of the pipe line connecting the mixing chambers 26 a and 26 f, and the pipeline connecting the heat exchanger 10 and the pipe line connecting the mixing chambers 26 a and 26 f. Therefore, the cooling medium cooled in the mixing tank 26 can be supplied to the heat exchanger 10 selectively from the mixing chambers 26 a and 26 f. For example, an electromagnetic 3-way valve activated electrically to switch the flow channel can be used as the switching valve 33.

In order to supply the cooling medium from the mixing chambers 26 a and 26 f to the heat exchanger 10, and to return the cooling medium from the heat exchanger 10 to the mixing chamber 26 a, a pump 34 is arranged between the heat exchanger 10 and the switching valve 33. In this example, a conventional feeding pump is used as the pump 34.

In addition, although not shown in FIG. 2, the cooling system of the second example is further provided with a temperature detecting means adapted to detect the temperatures of the cooling mediums in the mixing chambers 26 a and 26 f, and a control means adapted to control the switching valve 33 and a below-explained switching valve 35 according to the temperature detected by the temperature detecting means. Therefore, the switching valve 33 is activated to switch a supply source of the cooling medium to the heat exchanger 10 between the mixing chambers 26 a and 26 f, in accordance with a signal from the control means representing the temperatures of the cooling mediums in the mixing chambers 26 a and 26 f. Specifically, in case the temperature of the cooling medium in the mixing chamber 26 a is higher than a predetermined temperature, the switching valve 33 allows the cooling medium in the mixing chamber 26 f to be supplied to the heat exchanger 10. Conversely, in case the temperature of the cooling medium in the mixing chamber 26 a is lower than a predetermined temperature, the switching valve 33 allows the cooling medium in the mixing chamber 26 a to be supplied to the heat exchanger 10. Alternatively, in order to switch the flow channels in the above-described manner to supply the cooling medium to the heat exchanger 10, a valve configured to be switched by a motor or the like may also be used as the switching valve 33 instead of the electromagnetic valve. Thus, the switching valve 33 serves as the first switching valve of the present invention.

As described, the chiller unit 11 is also connected with the mixing chambers 26 a and 26 f through the pipelines, and a switching valve 35 is arranged at a junction of the pipe line connecting the mixing chambers 26 a and 26 f, and the pipeline connecting the chiller unit 11. Therefore, the cooling medium in the mixing tank 26 can also be supplied to the chiller unit 11 selectively from the mixing chambers 26 a and 26 f, and the cooling medium cooled in the chiller unit 11 is returned to the mixing chamber 26 f. Here, the structure of the switching valve 35 is identical to that of the switching valve 33. Therefore, in case the temperature of the cooling medium in the mixing chamber 26 f is higher than a predetermined temperature, the switching valve 35 is switched by the control means in a manner to allow the cooling medium in the mixing chamber 26 f to be supplied to the chiller unit 11. Conversely, in case the temperature of the cooling medium in the mixing chamber 26 f is lower than a predetermined temperature, the switching valve 35 is switched by the control means in a manner to allow the cooling medium in the mixing chamber 26 a to be supplied to the chiller unit 11. Thus, the switching valve 35 serves as the second switching valve of the present invention.

In order to supply the cooling medium to the chiller unit 11 from the mixing chambers 26 a and 26 f, and to return the cooling medium from the chiller unit 11 to the mixing chamber 26 f, a pump 36 is arranged between the switching valve 35 and the chiller unit 11. Here, a conventional pump is also used to serve as the pump 36.

As in the first example, the chiller unit 11 is also connected with the cooling tower 16 erected outside of the cooling system through pipelines forming a circuit, and in order to circulate cooling water in the circuit, a pump 37 is arranged on the pipeline for feeding the cooling water from the chiller unit 11 to the cooling tower 16. Therefore, the heat of the chiller unit 11 is transported to the cooling tower 16 by the cooling water, and radiated to the atmosphere from the cooling tower 16 by the fan 17.

Thus, according to the second example of the present invention, the heat of the electronic component 8 is transported to the heat exchanger 10 by the cooling medium circulating in the circuit connecting the cold plate 9 and the heat exchanger 10. The heat thus transported to the heat exchanger 10 is transferred to the cooling medium supplied to the heat exchanger 10 from the mixing chamber 26 a or 26 f which is cooled by the ice storage device 27 or by the chiller unit 11. The cooling medium warmed in the heat exchanger 10 is returned to the mixing chamber 26 a of the mixing tank 26, and gradually cooled in the mixing tank 26 while flowing across the mixing chambers 26 a to 26 f to be mixed convectively with the cooling medium flowing from the mixing chamber 26 f which is cooled by the ice storage device 27 or the chiller unit 11. Then, the cooling medium whose temperature is thus neutralized in the mixing tank 26 is supplied again to the ice storage device 27 and to the chiller unit 11. Therefore, according to the second example, the cold energy in the ice storage device 27 will not be wasted excessively, that is, the ice stored in the ice storage device 27 will not be melted excessively. In addition to the above-explained advantage, the burden of the chiller unit 11 can be lightened so that the running cost of the chiller unit 11 and CO₂ emission can be reduced. Conversely, according to the cooling system of the second example, it is also possible to warm the cooling medium in the mixing tank 26 in advance, and supply the warmed cooling medium to the heat exchanger 10. In this case, the electronic component 8 can be prevented from being cooled excessively.

That is, according to the cooling system of the second example, temperature of the cooling medium to be supplied to the heat exchanger 10, the chiller unit 11 and the ice storage device 27 can be optimized in the mixing tank 26 before supplied to those elements. Therefore, thermal efficiency of the cooling system can be improved. In addition, the temperature of the cooling medium to be supplied to the heat exchanger 10, the chiller unit 11 and the ice storage device 27 from the mixing tank 26 can be adjusted more finely by changing a number of the mixing chambers in the mixing tank 26. Further, according to the second example of the present invention, the electronic component 8 can be cooled only by the ice storage device 27 even if the chiller unit 27 is in trouble or electric power supply to the chiller unit 11 is interrupted.

Next, the third example of the present invention will be explained hereinafter with reference to FIG. 3. Specifically, the third example of the present invention relates to an auxiliary cooling device, which is configured to cool the datacenter 1 in case the chiller unit 11 functioning as the main cooling device is in trouble due to electric power outage or the like.

According to the third example, the server racks 3 are also installed in the container 2 of the datacenter 1. The cold plate 9 is also contacted with the electronic component 8 and connected with the heat exchanger 10 through the pipelines forming a circuit, and the pump 25 is arranged on the pipeline for returning the cooling medium from the cold plate 9 to the heat exchanger 10. Therefore, the cooling medium can be circulated in the circuit connecting the cold plate 9 and the heat exchanger 10.

According to the third example, the heat exchanger 10 is connected with the evaporator 15 of the chiller unit 11 thorough pipelines forming a circuit, and in order to circulate the cooling medium in the circuit, a pump 38 is arranged on the pipeline for supplying the cooling medium from the chiller unit 11 to the heat exchanger 10. Therefore, the heat of the electronic component 8 is transferred to the cold plate 9, and the heat transferred to the cold plate 9 is transported to the heat exchanger 10 by the cooling medium. The heat of the cooling medium thus transported to the heat exchanger 10 from the cold plate 9 is then transferred to the cooling medium having lower temperature supplied to the heat exchanger 10 from the chiller unit 11. As a result, the electronic component 8 is cooled by the cold plate 9.

Meanwhile, the condenser 13 of the chiller unit 11 is connected with the cooling tower 16 through pipelines forming a circuit, and in order to circulate cooling water in the circuit, a pump 37 is arranged on the pipeline for supplying the cooling medium from the condenser 13 to the cooling tower 16. The heat of the cooling medium warmed in the condenser 13 is transported to the cooling tower 16, and radiated to the atmosphere by the fan 17.

In the circuit connecting the heat exchanger 10 and the chiller unit 11, a switching valve 39 is arranged at a junction of the pipeline for supplying the cooling medium from the heat exchanger 10 to the evaporator 15 and a pipeline for supplying the cooling medium from said pipeline to an ice storage device 41 functioning as an auxiliary cooling device. In addition, a switching valve 40 is arranged at a junction of the pipeline for supplying the cooling medium from the evaporator 15 to the heat exchanger 10 and a pipeline for supplying the cooling medium from the ice storage device 41 to said pipeline. Therefore, according to the third example, the ice storage device 41 can be used as the cold source for cooling the datacenter 1 instead of the chiller unit 11, in case the chiller unit 11 has some kind of trouble.

Thus, the cooling medium warmed in the heat exchanger 10 is allowed to flow selectively to the chiller unit 11 and to the ice storage device 41 by switching the switching valve 39. Likewise, the cooling medium cooled in the chiller unit 11 is allowed to flow selectively to the heat exchanger 10 and to the ice storage device 41 by switching the switching valve 40.

Although not especially shown in FIG. 3, according to the third example, the cooling system is provided with: a detecting means adapted to detect a change in the temperature of the datacenter 1 and to detect a trouble in the chiller unit 11; and a control means adapted to switch the switching valves 39 and 40 on the basis of a detection signal from the detecting means. Therefore, in case the temperature in the datacenter 1 detected by the detecting means is higher than a predetermined temperature, or in case a trouble in the chiller unit 11 is detected by the detecting means, the switching valve 39 is switched by the control means to allow the cooling medium in the heat exchanger 10 to flow toward the ice storage device 41, and the switching valve 40 is switched by the control means to allow the cooling medium in the ice storage device 41 to flow toward the heat exchanger 10. As described, an electromagnetic valve can be used as the switching valves 39 and 40. According to the third example, since the aforementioned pump 38 is arranged between the switching valve 40 and the heat exchanger 10, the cooling medium can be circulated among the heat exchanger 10, the chiller unit 11 and the ice storage device 41 without arranging additional pumps.

As the examples previously explained, the ice storage device 41 comprises: a tank 42 which reserves the cooling medium therein; and a plurality of heat pipes 43. In order to insulate the cooling medium stored in the ice storage device 41, tank 42 is preferably formed of low-heat conductive material such as concrete.

According to the third example, a thermosiphon is also used as the heat pipe 43. Therefore, a direction of the heat pipe 43 to transport the heat is restricted to one direction, and the external heat will not enter into the tank 41 through the heat pipe 43. Also, the working fluid encapsulated in the heat pipe 43 is selected from ammonia and hydrochlorofluorocarbon such as R-134 or the like whose boiling point is lower than 10 degrees C., and 20 to 30 volume percent of the working fluid is contained in the heat pipe 43.

The heat pipe 43 is erected substantially vertically in the tank 42, and one of the end portions of the heat pipe 43 immersed into the cooling medium in the tank 42 serves as an evaporating portion 43 a at which working fluid encapsulated therein is heated to be vaporized. The other end portion of the heat pipe 43 is exposed to outside of the tank 42 to be contacted with the atmosphere. That is, the other end portion serves as a condensing portion 43 b at which the vaporized working fluid in the heat pipe 43 is condensed by radiating the heat of the vaporized working fluid to the atmosphere. For this purpose, a plurality of radiating fins 44 are arranged on the condensing portion 43 b. The working fluid thus condensed in the condensing portion 43 b is gravitationally returned to the evaporating portion 43 a. In order to freeze the cooling medium stored in the tank 42 efficiently, the ice storage device 41 is preferably installed in a cold region where a freezing index is higher than 400 degree C.·day.

In case the temperature of the cooling medium in the ice storage device 41 is higher than the external temperature, and the external temperature becomes lower than a predetermined operating temperature of the heat pipe 43, the heat of the cooling medium in the tank 42 is transported in the heat pipe 43 from the evaporating portion 43 a to the condensing portion 43 b, and radiated to the atmosphere from the fins 44. As a result, the cooling medium in the tank 42 is cooled to store the cold energy, and in case the external temperature further drops to below freezing point, the cooling medium in the ice storage device 41 is frozen. Conversely, even in case the external temperature becomes higher than the temperature of the cooling medium in the tank 42, the external heat will not enter into the ice storage device 41 through the heat pipe 43 so that the cooling medium can be prevented from being wasted by the external air.

Thus, according to the third example of the present invention, the cold energy can be stored in the ice storage device 41 utilizing the external cold energy without using electricity. That is, the ice storage device 41 can be operated without running cost and without emitting CO₂ gas. Moreover, the cold energy is stored in the ice storage device 41 in the form of ice. Therefore, the ice storage device 41 can be downsized in comparison with a case of storing the cold energy by merely cooling liquid phase cooling medium so that a construction cost thereof can be reduced. In addition to the above-explained advantages, the cold energy stored in the ice storage device 41 can be supplied to the heat exchanger 10 to cool the heated cooling medium returned to the heat exchanger 10 from the cold plate 9, in case electric power supply to the chiller unit 11 is interrupted, or in case a failure occurs in the chiller unit 11. Thus, the ice storage device 41 serves as the auxiliary cooling device of the present invention.

Next, here will be explained a fourth example of the present invention with reference to FIGS. 4 to 10. The fourth example is a modified example of the auxiliary cooling device used in the third example. Therefore, detailed explanation for the elements in common with the previously explained example is omitted by allotting common reference numerals. FIG. 4 is a schematic view showing an entire structure of the cooling system for a datacenter using the modified auxiliary cooling device according to the fourth example. As shown in FIG. 4, in the fourth example, the heat exchange 10 is not interposed between the data center 1 and the chiller unit 11 unlike the third example. However, it is possible to interpose the heat exchanger 10 between the data center 1 and the chiller unit 11 according to need.

Specifically, in the fourth example, the cold plate 9 is connected with the chiller unit 11 through a feeding pipe for supplying the cooling medium from the chiller unit 11 to the cold plate 9, and the switching valve 39 is arranged on the feeding pipe. Therefore, the cooling medium cooled by the chiller unit 11 is supplied to the cold plate 9 via the switching valve 39. The cold plate 9 is also connected with the chiller unit 11 through a returning pipe for returning the cooling medium from the cold plate 9 to the chiller unit 11, and the switching valve 40 is arranged on the returning pipe. Therefore, heat of the electric component 8 transferred to the cold plate 9 is transported to the chiller unit 11 by the cooling medium through the returning pipe via the switching valve 40.

In addition, another feeding pipe of the cooling medium is also extended from the ice storage device 41 and merged with the feeding pipe extending from the chiller unit 11 at the switching valve 39. Meanwhile, the returning pipe extending from the cold plate 9 is divided at the switching valve 40 to be also connected with the ice storage device 41. Therefore, it is possible to form a circuit connecting the cold plate 9 and the chiller unit 11, and a circuit connecting the cold plate 9 and the ice storage device 41 alternately by switching the switching valves 39 and 40.

In order to force the cooling medium to circulate in each of the circuits, that is, among the cold plate 9, the chiller unit 11 and the ice storage device 41, the pump 25 is arranged between the switching valve 39 and the cold plate 9.

Thus, according the fourth example, the cooling medium can be circulated alternately in the circuit connecting the cold plate 9 and the chiller unit 11, and in the circuit connecting the cold plate 9 and the ice storage device 41 by switching the switching valves 39 and 40 by the control means. Therefore, the cooling medium heated by the heat of the electronic component 8 in the cold plate 9 can be returned selectively to the chiller unit 11 and the ice storage device 41, and the cooling medium cooled in the chiller unit 11 or the ice storage device 41 can be supplied to the cold plate 9 selectively depending on the temperature in the data center 1 or depending on an operating condition of the chiller unit 11.

As shown in FIG. 5, in order to insulate the ice storage device 41 from the external heat, the ice storage device 41 according to the fourth example is buried in the ground where the temperature change is smaller than that above the ground, and the ice storage device 41 is surrounded by a heat insulating layer 45 below the ground, which in turn is surrounded by a waterproof layer 46. FIG. 6 is a schematic view showing an outlook of the ice storage device 41 of the fourth example, and FIG. 7 is a sectional view thereof. As shown in FIG. 7, according to the fourth example, the ice storage device 41 comprises: cold storage medium to be frozen by the external cold energy; the tank 42 which holds cold storage medium therein; a heat insulating layer 45 which insulate the tank 42 from the external heat; a waterproof layer 46 which prevent external water from penetrating into the tank 42; the plurality of heat pipes 43 which radiates the heat of cold storage medium reserved in the tank 42 to the atmosphere, and a coil shaped heat exchanging tube 49 is wrapped around the evaporating portion 43 a of the heat pipe 43. A shape of the tank 42 should not be limited to a specific shape. However, in case of forming the tank 42 into a cylindrical shape as shown in FIG. 6, a surface area of the tank 42 can be reduced in comparison with a case of forming the tank 42 into a cuboid shape having a same capacity.

FIG. 8 is a close-up showing the cross section of the ice storage device 41 of the fourth example partially in an enlarged scale. As shown in FIG. 8, the heat insulating layer 45 comprises an inner layer 47 formed of a hollow plate; and an outer layer 48 formed of porous material. Specifically, a conventional hollow vacuum panel in which an internal pressure thereof is lower than an atmospheric pressure can be used as the inner layer 47, and the outer layer 48 can be formed of expanded polyurethane, expanded polystyrene, glass wool etc.

As described, in order to prevent the external water from penetrating into the tank 42, the waterproof layer 46 is formed around the outer layer 48. For example, a waterproof sheet formed of synthetic resin can be used as the waterproof layer 46.

An example of a coil shaped heat exchanging tube 49 adapted to transport the cold energy from the cold storage medium in the tank 42 is shown in FIG. 9. Specifically, the heat exchanging tube 49 is a hollow tube wrapped spirally around the evaporating portion 43 a of the heat pipe 43, and the liquid phase cooling medium is allowed to flow therethrough. In order to facilitate heat exchange between the heat of the liquid phase cooling medium flowing through the heat exchanging tube 49 and the cold energy of the cold storage medium in the tank 42, material of the heat exchanger 49 is selected from copper, copper alloy, aluminum, aluminum alloy and so on. A length of the heat exchanging tube 49 can be adjusted according to a required amount of the cold energy for cooling the datacenter 1 to a desired temperature, in other words, according to an amount of the heat to be exchanged between the cooling medium and the cold storage medium thorough the heat exchanging tube 49. A length of the heat exchanging tube 49 required in the ice storage device 41 can be experimentally found in advance. In addition, in order to reduce a cost of the material, the heat exchanging tube 49 may also formed of synthetic resin. In this case, heat conductivity of the heat exchanging tube 49 has to be degraded, however, such disadvantage can be avoided by elongating the length of the heat exchanging tube 49.

In case the switching valve 39 and 40 are switched in a manner to connect the cold plate 9 and the ice storage device 41, the cooling medium heated as a result of drawing the heat of the electronic component 8 in the cold plate 9 is returned to the ice storage device 41 through the aforementioned returning pipe. The cooling medium entering into the heat exchanging tube 49 flows from an upper side of the heat exchanging tube 49 toward a lower side of the heat exchanging tube 49 while transferring the heat thereof to the cold storage medium in the tank 42. As a result, the liquid phase cooling medium flowing through the heat exchanging tube 49 is cooled by the cold energy of the cold storage medium in the tank 42, and then supplied to the cold plate 9.

In case the external temperature drops to below the freeing point, the cold storage medium in the tank 42 is frozen by the external cold energy entering into the tank 42 through the heat pipes 43. In this case, first the cold storage medium around a surface of the evaporating portion 43 a starts to be frozen as illustrated by a dotted line in FIG. 10. Then, the cold storage medium around the heat exchanging tube 49 is frozen, and eventually the cold storage medium in the tank 42 is frozen entirely. The external cold energy is thus stored in the tank 42 in the form of ice.

Specifically, in case the detecting means detects that the temperature in the datacenter 1 is higher than a predetermined temperature, or that the chiller unit 11 cannot be operated, the switching valves 39 and 40 are switched by the control means in a manner to switch a cold energy source used to cool the datacenter 1 from the chiller unit 11 to the ice storage device 41. In this case, the cooling medium heated by the electronic component 8 in the cold plate 9 is returned to the heat exchanging tube 49 in the ice storage device 41 through the returning pipe. As a result, the heat of the cooling medium flowing through the heat exchanging tube 49 is transferred to the frozen cold storage medium in the tank 42, and the temperature of the cooling medium is lowered while melting the frozen cold storage medium. The cooling medium thus cooled in the ice storage device 41 is then supplied to the cold plate 9 thorough the feeding pipe thereby cooling the electronic component 8.

Thus, according to the fourth example of the present invention, the cold energy of the cold storage medium held in the ice storage device 41 can be transported easily by the liquid phase cooling medium flowing through the heat exchanging tube 49, even when the cold storage medium is frozen. In addition, the ice storage device 41 of the fourth example is buried in the ground, and covered by the heat insulating layer 45 and the waterproof layer 46. Therefore, the cold energy stored in the ice storage device 41 can be prevented from being wasted by the external heat, and the external water will not penetrating into the tank 42.

Moreover, the ice storage device 41 functioning as the auxiliary cooling device of the fourth example is configured to store the cold energy by freezing the cold storage medium stored therein only using the external cold energy. Therefore, in addition to the above-explained advantages, a layout of the cooling system for the datacenter can be altered flexibly and more easily in comparison with a cooling system for the datacenter using a conventional chiller unit adapted to cool the cooling medium electrically. For example, even in the case where the number of computer servers is increased and larger output of the cold energy is therefore required, the output of the ice storage device 41 can be easily increased by merely increasing the number of heat pipes 43. In this case, the output of the ice storage device 41 can be increased without expanding an installation area of the ice storage device 41. Alternatively, it is also possible to introduce additional ice storage devices 41 easily according to the required cold energy. Further, the conventional chiller unit used as the auxiliary cooling device in the conventional cooling system can be replaced easily by the cold storage device 41 of the present invention.

Next, here will be explained a fifth example of the present invention with reference to FIGS. 11 to 15. The fifth example is another modified example of the auxiliary cooling device used in the third example. That is, a relation of connection of the elements constituting the cooling system is identical to those of the third and the fourth example shown in FIGS. 3 and 4. Therefore, detailed explanation for the elements in common with the previously explained example is omitted by allotting common reference numerals.

The ice storage device 41 of the fifth example is preferably used as the auxiliary cooling device for the datacenter whose electrical power consumption is approximately 200 kWh. For this purpose, according to the fifth example, the ice storage device 41 is also buried in the ground, and in order to insulate the ice storage device 41 more effectively from the external heat thereby retaining the cold energy therein more efficiently, the ice storage device 41 of the fifth example is further provided with a soil layer 52 covering the tank 42.

As shown in FIG. 12, the ice storage device 41 of the sixth example is also shaped into a cylindrical shape, and a soil layer 52 is formed around the ice storage device 41. FIG. 13 is a sectional view showing a cross section of the ice storage device 41 shown in FIG. 12. Specifically, as shown in FIG. 13, a maintenance room 50 is formed around the tank 42 of the ice storage device 41. The soil layer 52 is held by a bottomed cylindrical wooden support 53. In order to retain the soil and the water in the soil layer 52, the waterproof layer 46 is interposed between the soil layer 52 and the wooden support 53. In order to radiate the heat in the soil layer 52, according to the fifth example, a plurality of another heat pipes 54 is buried in the soil layer 52 substantially vertically at predetermined intervals. Specifically, a thermosiphon is also used as the heat pipe 54, therefore, a direction of the heat pipe 54 is restricted to one direction by a thermal diode characteristics thereof. That is, the external heat will not enter into the soil layer 52 through the heat pipes 54. As shown in FIG. 14, an entrance 51 is formed in the maintenance room 50 so that a worker is allowed to enter into the maintenance room 50. In addition, the soil layer 52 is formed around the maintenance room 50, and underneath the maintenance room 50 and the tank 42. Specifically, the soil layer 52 contains 5 to 20 percent of moisture, and a thickness thereof is approximately 1 meter. Further, according to the fifth example, the aforementioned heat insulating layer 45 is formed around the wooden support 53 and underneath the bottom of the wooden support 53. Additionally, as shown in FIG. 14, the ice storage device 41 is covered with a shield 57.

As shown in FIG. 15, a portion of the heat pipe 54 buried in the soil layer 52 serves as an evaporating portion 54 a, and other end portion of the heat pipe 54 is exposed to outside of the soil layer 52 to be contacted with the atmosphere serves as a condensing portion 54 b. In order to radiate the heat of the soil layer 52 to the atmosphere from the condensing portion 54 b, a plurality of fins 55 are arranged on the condensing portion 54 b. Remaining structures of the heat pipe 54 are identical to those of the aforementioned heat pipe 43. Therefore, a detailed explanation for the structure and function of the heat pipe 54 in common with those of the heat pipe 43 will be omitted. However, in order to prevent a corrosion of the heat pipe 54, the heat pipe 54 may be made of corrosive-resistant material such as stainless. In addition, in order to radiate the heat in the bottom part of the soil layer 52 to the atmosphere, as shown in FIG. 15, the evaporating portion 54 a of the heat pipe 54 is bent at a vicinity of the bottom of the maintenance room 50 toward the center of the tank 42. Here, in order to gravitationally return the working fluid to the end of the evaporating portion 54 a, the bent portion of evaporating portion 54 a is preferably tilted at approximately 5 degrees.

In the fifth example, sand, loam and clay can be used as a material of the soil layer 52, and moisture content of those materials are 2.5 to 10 percent, 10 to 17.5 percent, and 17.5 to 25 percent, respectively. Therefore, in case of forming the soil layer 52 mainly using sand, it is preferably to keep the moisture content of the soil layer 52 within a range of 2.5 to 10 percent. Consequently, the soil layer 52 can be frozen and strength of the soil layer 52 can be enhanced by radiating the heat thereof to the atmosphere through the heat pipes 54. Likewise, in case of forming the soil layer 52 using loam or clay, the moisture content thereof are preferably kept to the above-mentioned ranges respectively.

Next, here will be explained a function of the ice storage device 41 according to the fifth example. As in the previously explained examples, in case the temperature of the cold storage medium in the ice storage device 41 becomes higher than the external temperature, and the external temperature becomes lower than a predetermined temperature, the working fluid in the evaporating portion 43 a of the heat pipe 43 is vaporized by the heat of the cold storage medium stored in the tank 42, and the heat of the cold storage medium is transported to the condensing portion 43 b in the form of the latent heat of the working fluid. The heat of the cold storage medium thus transported to the condensing portion 43 b is radiated to the atmosphere through the fins 44, and the condensed working fluid is returned gravitationally to the evaporating portion 43 a. As a result, the cold storage medium in the tank 42 is cooled. In this situation, in case the external temperature further drops to below freezing point, the cooling medium in the ice storage device 41 is frozen by the same principle explained in the fourth example.

Likewise, in case the temperature of the soil layer 52 becomes higher than the external temperature, and the external temperature becomes lower than a predetermined operating temperature of the heat pipe 54, the working fluid in the evaporating portion 54 a of the heat pipe 54 is vaporized by the heat of the soil layer 52, and the heat of the soil layer 52 is transported to the condensing portion 54 b by the vaporized working fluid in the form of the latent heat. The heat of the soil layer 52 thus transported to the condensing portion 54 b is radiated to the atmosphere through the fins 55. Therefore, working fluid is condensed again in the condensing portion 54 b, and returned gravitationally to the evaporating portion 54 a. As a result, the soil layer 52 is cooled to store the cold energy therein. Also, in case the external temperature further drops to below the freezing point, the soil layer 52 is further cooled and frozen. As a result, the soil layer 52 becomes a permafrost layer. Conversely, since the thermosiphon is used as the heat pipe 54, the heat pipe 54 will not transport the heat in case the temperature of the soil layer 52 becomes lower than the external temperature, and the external temperature becomes higher than a predetermined temperature.

Thus, the ice storage device 41 of the fifth example is further provided with the soil layer 52 having approximately 1 meter thickness, and the plurality of heat pipes 54 are buried therein. In addition, the soil layer 52 is covered by the heat insulating layer 45, and the ice storage device 41 is installed in a cold region where a freezing index is higher than 400 degree C.·day. Therefore, in addition to the advantages achieved by the ice storage device 41 according to the third and the fourth examples, according to the fifth example, the soil layer 52 frozen by the heat pipes 54 can be kept to be frozen throughout the year. That is, the cold energy stored in the tank 42 by freezing the cold storage medium held therein can also be retained throughout the year by the soil layer 52 as a permafrost layer. The cold energy thus stored in the ice storage device 41 can be used to cool the datacenter 1 anytime when the chiller unit 11 is in trouble.

Next, here will be explained a modified example of the ice storage device 41 of the fifth example with reference to FIGS. 16 to 18. The modified ice storage device 41 of the fifth example is to be used as the auxiliary cooling device for the datacenter whose electrical power consumption is smaller than 200 kWh. Therefore, according to the modified example of the fifth example, the tank 42 is relatively smaller than that used in the previously explained ice storage device 41, and as shown in FIG. 16, the ice storage device 41 is covered with a shield 57. In addition, a U-shaped heat exchanging tube 56 is used instead of the coil-shaped heat exchanging tube 49.

Specifically, as shown in FIG. 16, most of the modified ice storage device 41 of the fifth example is buried in the ground, and the portion of the ice storage device 41 thus buried is covered with the shield 57. A clearance between the soil layer 52 and the shield 57 is filled with another soil. An upper portion of the ice storage device 41 exposed above the ground level is covered with a lid 58. In order to insulate the portion of the ice storage device thus exposed, the lid 58 is preferably made of heat insulating material such as concrete. The heat exchanging tube 56 is a hollow tube made of heat conductive material such as copper, copper alloy, aluminum, aluminum alloy and so on, and the liquid phase cooling medium flowing from the cold plate 9 flows therethrough. According to the modified example of the fifth example, the heat exchanging tube 56 thus structured is bent into U-shape, and arranged in the vicinity of the evaporating portion 54 a of the heat pipe 54. Therefore, the heat of the liquid phase cooling medium flowing through the heat exchanging tube 56 is drawn by the cold storage medium in the tank 42.

In case of using the ice storage device 41 in the datacenter whose electrical power consumption is larger than 200 kWh, thereby requiring larger output of the ice storage device 41, a capacity of the ice storage device 41 can be increased easily by merely combining a plurality of the ice storage devices 41 to form a larger auxiliary cooling system having a required capacity. An example of combining three ice storage devices 41 in the shield 57 is shown in FIG. 17, and FIG. 18 is a cross sectional view thereof. Although not especially shown in FIGS. 17 and 18, both of the coil shaped heat exchanging tube 49 and the U-shaped heat exchanging tube 56 can be used in this example.

As shown in FIG. 17, each of the three ice storage device 41 is formed into a cuboid shape, and the plurality of heat pipes 43 are erected in the ice storage device 41. In this example, each of the ice storage devices 41 is covered with the heat insulating layer 45 and the waterproof layer 46. The ice storage devices 41 thus unified is enclosed entirely by the soil layer 52. As described, a thickness of the soil layer 52 is preferably 1 meter, and the plurality of heat pipes 54 are erected in the soil layer 52. However, in case of combining the plurality of ice storage devices 41 in this manner, a thickness of a soil layer 52 between the adjoining ice storage devices 41 can be reduced to be smaller than 1 meter.

Thus, the capacity of the ice storage device 41 can be increased easily by merely combining a plurality of the ice storage devices 41. Therefore, even in the case where a number of the computer servers is increased and larger output of the auxiliary cooling device 41 is required, the larger cold energy can be stored in the auxiliary cooling device 41 by increasing the number of the ice storage device 41 without introducing additional air conditioners and chiller units. In addition, the cold energy of the frozen soil layer 52 can also be utilized to cool the datacenter 1 by merely arranging the coil shaped heat exchanging tube 49 or the U-shaped heat exchanging tube 56 in the soil layer 52.

Next, an assist heat pipe according to the sixth example of the present invention will be explained with reference to FIG. 19. In the example shown in FIG. 19, a plurality of server racks 3 housing a plurality of computer servers therein are installed in the housing of the datacenter 1, and the housing 2 is provided with an air conditioner 4 for the purpose of cooling the computer servers by lowering a temperature in the housing 2 raised by the electronic components of the servers. In addition, in order to assist the air conditioner 4 by radiating the heat in the housing 2 to the atmosphere, the heat pipe 5 is arranged in the housing 2 above the server rack 3 in the direction of gravitational force.

Specifically, as the heat pipes used in the above-explained examples, the assist heat pipe 5 is also a thermosiphon comprising an evacuated hollow container, and volatile and condensable working fluid contained in the container air-tightly. In order to exchange internal heat and external cold energy efficiently, the container of the assist heat pipe 5 is also made of material having good heat conductivity such as copper. In addition, the working fluid of the assist heat pipe 5 is selected from water, ammonia and hydrochlorofluorocarbon and so on depending on a condition of temperature.

Specifically, according to the example shown in FIG. 19, one of end portions of the assist heat pipe 5 extending parallel to the ceiling of the housing 2 above the server rack 3 serves as the evaporating portion 5 a at which the working fluid is heated to be vaporized by the internal heat of the housing 2. The assist heat pipe 5 is bent at a substantially right angle while penetrating through the ceiling to be exposed to the outside of the housing 2. The other end portion of the assist heat pipe 5 thus exposed to the outside of the housing 2 to be contacted with the external air serves as the condensing portion 5 b at which the vaporized working fluid is condensed by radiating the heat thereof to the atmosphere. In addition, a plurality of fins 6 for radiating and receiving the heat is arranged on both of the evaporating portion 5 a and the condensing portion 5 b. Here, the fins 6 are also formed of heat conductive material.

Therefore, in case the internal temperature of the housing 2 is raised by the electronic components to be higher than the external temperature, or in case the external temperature becomes lower than the internal temperature of the housing 2, the working fluid is vaporized in the evaporating portion 5 a of the assist heat pipe 5. The vapor of the working fluid rises toward the condensing portion 5 b where the temperature and the pressure are lower than those in the evaporating portion 5 a, and the internal heat of the housing 2 thus transported to the condensing portion 5 b by the vaporized working fluid is then radiated to the atmosphere thorough the fins 6. As a result, the vaporized working fluid is condensed again in the condensing portion 5 b and returned gravitationally to the evaporating portion 5 a. Thus, a thermal diode characteristic of the assist heat pipe 5 also ensures transport of the heat unilaterally from evaporating portion 5 a toward the condensing portion 5 b thereby radiating the internal heat of the housing 2 unilaterally to the outside of the housing 2. For this reason, the external heat will not enter into the housing 2 through the assist heat pipe 5.

Thus, according to the sixth example, the inner space of the housing 2 is cooled by transporting the internal heat of the housing 2 outside of the housing 2 through the assist heat pipe 5 under the condition in which the internal temperature of the housing 2 is higher than the external temperature. Therefore, a burden on the air conditioner 4 can be lightened so that an operating time of the air conditioner 4 can be shortened. As a result, an electric consumption of the air conditioner 4 is reduced so that CO₂ emission can be reduced. In addition, since the external heat will not enter into the housing 2 thorough the assist heat pipe 5, the internal temperature of the container 2 can be prevented from being raised by the external heat.

Although the above exemplary embodiments of the present invention have been described, it will be understood by those skilled in the art that the present invention should not be limited to the described exemplary embodiments, but that various changes and modifications can be made within the spirit and scope of the present invention. 

1. A cooling system for a data center, in which a plurality of servers having exothermic electronic components is installed in a housing, comprising: a circuit, in which a cooling medium is circulated therethrough; a main cooling device, which is connected with the electronic components through the circuit, and to which the cooling medium heated by drawing heat from the electronic components is returned; and an auxiliary cooling device, which is arranged on a return pipe of the circuit between the main cooling device and the electronic components to assist the main cooling device in cooling the cooling medium.
 2. The cooling system for a data center according to claim 1, wherein: the auxiliary cooling device comprises a tank which stores the cooling medium therein, and a first plurality of heat pipes which are adapted to cool or freeze the cooling medium by radiating heat of the cooling medium to the atmosphere; wherein the first plurality of heat pipes comprise thermosiphons, in which a volatile and condensable working fluid is encapsulated air-tightly; wherein one of end portions of the thermosiphons are immersed into the cooling medium in the tank to serve as an evaporating portion; and the other end portion of the thermosiphons are exposed to the atmosphere to serve as a condensing portion; and, wherein the first plurality of heat pipes are arranged such that the condensed working fluid drops only gravitationally to unilaterally restrict the direction of transport of the heat.
 3. The cooling system for a data center according to claim 2, further comprising: a heat exchanger, which is arranged on the circuit between the electronic components and the main and auxiliary cooling devices to exchange the heat of the electronic components and cold energy of the cooling medium.
 4. The cooling system for a data center according to claim 2, further comprising: a cooling tower, which is connected with the main cooling device to radiate heat of the main cooling device to the atmosphere.
 5. The cooling system for a data center according to claim 2, wherein the auxiliary cooling device further comprises a flow channel letting through the cooling medium supplied to the tank unilaterally.
 6. The cooling system for a data center according to claim 2, further comprising: a mixing tank.
 7. The cooling system for a data center according to claim 6, wherein: the mixing tank is divided into a plurality of mixing chambers, and adjoining mixing chambers are connected by a through hole.
 8. The cooling system for a data center according to claim 7, further comprising: a first switching valve, which switches a route for feeding the cooling medium from the mixing tank to the electronic component between a route from said one of the mixing chamber to the electronic component, and a route from said another one of the mixing chamber to the electronic component; a first pump, which is arranged between the first switching valve and the electronic component to feed the cooling medium to the electronic component; a second switching valve, which switches a route for feeding the cooling medium from the mixing tank to the main cooling device between a route from said one of the mixing chamber to the main cooling device, and a route from said another one of the mixing chamber to the main cooling device; a second pump, which is arranged between the second switching valve and the main cooling device to feed the cooling medium to the main cooling device; and a third pump, which is arranged on a route between said one of the mixing chamber and the auxiliary cooling device to feed the cooling medium in said one of the mixing chamber to the auxiliary cooling device.
 9. The cooling system for a data center according to claim 2, further comprising: a first switching valve, which returns the cooling medium heated by heat of the electronic components selectively to the main cooling device and the auxiliary cooling device; and a second switching valve, which supplies the cooling medium to the electronic component selectively from the main cooling device and the auxiliary cooling device.
 10. The cooling system for a data center according to claim 9, further comprising: a first pump, which is arranged on the circuit connecting the electronic component and the heat exchanger to circulate the cooling medium therethrough; a second pump, which is arranged on the circuit connecting the heat exchanger and the main cooling device to circulate the cooling medium therethrough; and a third pump, which is arranged on the circuit connecting the main cooling device and the cooling tower to circulate the cooling medium therethrough.
 11. The cooling system for a data center according to claim 2, wherein the auxiliary cooling device further comprises: a heat insulating layer, which covers the tank to prevent the tank from being warmed by an external heat.
 12. The cooling system for a data center according to claim 2, wherein the auxiliary cooling device further comprises: a cold storage medium, which is sealed in the tank to be frozen by external cold energy entering into the tank through the thermosiphon; and a heat exchanging tube, which is arranged around the evaporating portion of the thermosiphon, and at which the cold energy of the frozen cold storage medium in the tank is transferred to the cooling medium flowing therethrough.
 13. The cooling system for a data center according to claim 11, wherein the heat insulating layer comprises: an inner layer formed of an evacuated panel in which an internal pressure is reduced to be lower than an atmospheric pressure; and an outer layer formed of heat insulating porous material.
 14. The cooling system for a data center according to claim 12, wherein: the heat exchanging tube includes a coil heat exchanger formed by winding a hollow tube around the evaporating portion of the thermosiphon.
 15. The cooling system for a data center according to claim 11, wherein the auxiliary cooling device further comprises: a soil layer containing predetermined moisture and covering the tank; and a second plurality of heat pipes which are buried in the soil layer at least partially to freeze the moisture in the soil layer by radiating the heat of the moisture unilaterally to the atmosphere, under the condition in which a temperature of the moisture in the soil layer is higher than an external temperature and the external temperature is lower than a predetermined temperature.
 16. The cooling system for a data center according to claim 15, wherein: said second plurality of heat pipes comprise thermosiphons, in which a volatile and condensable working fluid is encapsulated air-tightly; wherein one of end portions of the thermosiphons are buried in the soil layer to serve as an evaporating portion; and the other end portion of the thermosiphons are exposed to the atmosphere to serve as a condensing portion, and wherein the first plurality of heat pipes are arranged such that the condensed working fluid drops only gravitationally to unilaterally restrict the direction of transport of the heat.
 17. The cooling system for a data center according to claim 15, wherein: a thickness of the soil layer is approximately 1 meter.
 18. The cooling system for a data center according to claim 12, wherein: the heat exchanging tube includes a U-shaped heat exchanger formed by bending a hollow tube into U-shape and arranged in the vicinity of the evaporating portion of the thermosiphon.
 19. The cooling system for a data center according to claim 1, further comprising: an air conditioner, which is arranged in the housing to control the temperature in the housing thereby cooling the server; and an assist heat pipe, which transports heat in the housing unilaterally to the atmosphere thereby assisting the air conditioner; and wherein the assist heat pipe includes a thermosiphon, in which a volatile and condensable working fluid is encapsulated air-tightly; one of end portions of the thermosiphon is situated in the housing above the server in a direction of gravitational force, and the other end portion of the thermosiphon is exposed to the atmosphere; and, wherein the assist heat pipe is arranged such that the condensed working fluid drops only gravitationally to unilaterally restrict the direction of transport of the heat.
 20. The cooling system for a data center according to claim 1, wherein the auxiliary cooling device is buried in the ground in a cold region where a freezing index is higher than 400 degree C.·day.
 21. A process of cooling a data center, wherein the process comprises the steps of supplying the cooling medium heated by the electronic component, and the cooling medium cooled by the main cooling device or the auxiliary cooling device, to the mixing tank of the cooling system of claim 6 to regulate the temperature thereof; and selectively supplying the cooling medium mixed in the mixing tank to the main cooling device and the auxiliary cooling device to be cooled, and also to the electronic component.
 22. A process of cooling a data center, wherein the process comprises the steps of supplying the cooling medium heated by the electronic component to one of the mixing chambers connected with the electronic component; and supplying the cooling medium cooled by the main cooling device or the auxiliary cooling device to another one of the mixing chambers of claim 7 connected with the main cooling device and the auxiliary cooling device; and gradually mixing the cooling medium heated by the electronic component, and the cooling medium cooled by the main cooling device or the auxiliary cooling device, in the mixing tank while flowing across the mixing chambers.
 23. The cooling system for a data center according to claim 14, wherein: the material of the heat exchanging tube is selected from the group consisting of copper, copper alloy, aluminum, aluminum alloy, and synthetic resin.
 24. The cooling system for a data center according to claim 17, wherein: the material of the soil layer is selected from a group consisting of sand, loam and clay.
 25. The cooling system for a data center according to claim 24, wherein a moisture content of the soil layer is kept within a range of 2.5 to 10% when the soil layer is formed of sand, a moisture content of the soil layer is kept within a range of 10 to 17.5% when the soil layer is formed of loam, and a moisture content of the soil layer is kept within a range of 17.5 to 25% when the soil layer is formed of clay. 